WO2008135288A1 - Chaîne cinématique, en particulier pour véhicules à moteur - Google Patents

Chaîne cinématique, en particulier pour véhicules à moteur Download PDF

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Publication number
WO2008135288A1
WO2008135288A1 PCT/EP2008/003690 EP2008003690W WO2008135288A1 WO 2008135288 A1 WO2008135288 A1 WO 2008135288A1 EP 2008003690 W EP2008003690 W EP 2008003690W WO 2008135288 A1 WO2008135288 A1 WO 2008135288A1
Authority
WO
WIPO (PCT)
Prior art keywords
exhaust gas
gas turbine
compressor
output shaft
drive
Prior art date
Application number
PCT/EP2008/003690
Other languages
German (de)
English (en)
Inventor
Markus Kley
Steffen KÄMMERER
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Priority to US12/449,999 priority Critical patent/US8191371B2/en
Priority to EP08758414A priority patent/EP2142776B1/fr
Publication of WO2008135288A1 publication Critical patent/WO2008135288A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/005—Exhaust driven pumps being combined with an exhaust driven auxiliary apparatus, e.g. a ventilator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • F02B37/105—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump exhaust drive and pump being both connected through gearing to engine-driven shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/04—Mechanical drives; Variable-gear-ratio drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a drive train, in particular motor vehicle drive train, with a supercharged internal combustion engine.
  • Charging an internal combustion engine is understood to mean the provision of a so-called turbocharger, comprising an exhaust gas turbine in the exhaust gas stream of the internal combustion engine and a compressor in an air duct leading to the internal combustion engine, wherein the compressor is driven by means of the exhaust gas turbine, the latter extracting energy from the exhaust gas, and the Compressor air, which is sucked for the combustion of the fuel in the internal combustion engine from the environment and supplied to the internal combustion engine, pre-compressed.
  • two exhaust gas turbochargers are provided, that is, with two parallel or serially connected exhaust gas turbines, each driving a compressor for air for the internal combustion engine.
  • turbo-compound systems are known in which with an exhaust gas turbine, then usually called Abgasnostiurbine, the exhaust gas of the engine energy is withdrawn, is converted into drive power and a drive connection, in which a hydrodynamic coupling can be arranged, the Output shaft, in particular the crankshaft of the internal combustion engine is supplied.
  • the exhaust gas turbine is usually arranged in the flow direction in the exhaust gas behind the exhaust gas turbine of the turbocharger and between the two systems - turbocharger and turbo compound - there is no mechanical connection.
  • turbocharger systems are known in operating states with a low Exhaust gas flow, that is, at low speeds of the internal combustion engine, a so-called turbo lag.
  • turbo-compound systems are generally used in addition to turbocharger systems, thereby increasing the complexity and number of parts of the powertrain.
  • only the energy components in the exhaust gas flow are available to the exhaust gas turbine, which have not previously been withdrawn from the exhaust gas flow through the exhaust gas turbine of the turbocharger.
  • the turbo-compound systems have no significant influence on the desired avoidance of the turbo lag.
  • Document JP62195420 describes a drive train with a generator driven by an internal combustion engine.
  • the output shaft of the internal combustion engine is via a hydrodynamic clutch and a gearbox in a drive connection with a turbocharger compressor unit.
  • the turbocharger-compressor unit comprises an exhaust gas turbine and a compressor, which are arranged on a common shaft, wherein the shaft also carries a gear of the gearbox.
  • the exhaust gas turbine is charged with exhaust gas from the internal combustion engine, which is additionally heated with a burner.
  • the compressor charges the engine by compressing fresh air and supplying it to the engine via a charge air cooler.
  • the published patent application DE 10 2004 029 828 A1 describes an exhaust-gas turbocharger for an internal combustion engine with a compressor and a turbine, wherein the compressor and the turbine are non-rotatably connected via a shaft. Coaxial and in a drive connection with the turbocharger shaft, an electrical machine is provided which is operable both as a motor and as a generator. Via a belt drive or a gear transmission, the turbocharger shaft is further connected to the output shaft of the internal combustion engine.
  • the patent specification De 10 2005 003 714 B4 describes for a turbocompound system a switchable via a switchable clutch compressor.
  • the coupling can be designed as a hydraulically filled and emptied coupling. To function, it is urgent that the first Coupling half with the exhaust gas turbine and the second coupling half is connected to the compressor.
  • the invention has for its object to provide a drive train, in particular motor vehicle powertrain, which operates with respect to the fuel efficiency even more efficient than the aforementioned drive trains.
  • a drive train in particular motor vehicle powertrain
  • the problems mentioned should be avoided and advantageously also the occurrence of a turbo lag should be eliminated.
  • the drive train is to be improved in terms of its structural design, in particular with respect to a mechanical power transmission and a hydrodynamic power transmission.
  • the drive train according to the invention has an internal combustion engine with an output shaft, in particular a crankshaft.
  • the exhaust gas turbine of a turbocharger is arranged in the fresh air flow to the internal combustion engine of the compressor of the turbocharger.
  • it is a so-called supercharged combustion engine.
  • the exhaust gas turbine is additionally in a drive connection with an auxiliary unit of the drive train, for example a pump, a fan, an electric generator or the drive shaft of another unit.
  • the drive power of the exhaust gas turbine can be used not only to drive the compressor, but also to drive the at least one other auxiliary unit. If this is an accessory that is able to provide even a drive torque or drive power, at least in certain operating conditions, available, for example, an electric generator, the also can be operated by a motor, then can be transmitted from the accessory drive power to the exhaust gas turbine and / or, if a bypass of the exhaust gas turbine with respect to the power flow is provided to the compressor to avoid the occurrence of a turbo lag.
  • a hydrodynamic coupling is arranged, in particular a controllable hydrodynamic coupling, which provides a torsional vibration damping and thus the exhaust gas turbine, if, for example, a compressor, in particular reciprocating compressor, for example, a motor vehicle compressed air system, is driven as an accessory, protects against torsional vibrations ,
  • the hydrodynamic coupling according to the invention is connected between the exhaust gas turbine and the compressor, in other words arranged between the exhaust gas turbine and the compressor.
  • Such an arrangement is to be understood in particular as meaning embodiments in which the drive power flow from the exhaust gas turbine runs via the primary wheel of the hydrodynamic coupling, but in particular not via the secondary wheel, or in which the corresponding drive power flow via a rotary element connected non-rotatably to the primary wheel of the hydrodynamic coupling, in particular gear or pulley, which rotates at the same speed as the primary wheel and is advantageously connected directly to this, is made in one piece or is carried on a common shaft leads.
  • a so-called turbo-compound system is provided in the drive train, which however, in contrast to known designs, does not require an additional exhaust gas turbine or exhaust gas turbine.
  • this embodiment of the invention namely, an introduction of drive power to the crankshaft, wherein the drive power is obtained from exhaust energy from the exhaust turbine of the turbocharger and not provided by an addition to the turbocharger exhaust gas turbine, which is located in the exhaust stream behind the turbocharger.
  • the output shaft of the internal combustion engine or the internal combustion engine itself, the auxiliary unit which is driven by means of the exhaust gas turbine in addition to the compressor of the turbocharger.
  • drive power from the exhaust turbine of the turbocharger can either be selectively transmitted either exclusively to the compressor of the turbocharger or the output shaft, in particular crankshaft of the internal combustion engine.
  • a power transmission of drive power of the exhaust gas turbine of the turbocharger is simultaneously possible on the compressor and the output shaft of the internal combustion engine.
  • a hydrodynamic coupling is arranged in the drive connection between the output shaft and the exhaust gas turbine.
  • a hydrodynamic coupling has a bladed primary wheel, also called pump impeller, and a bladed secondary wheel, also called a turbine wheel, which together form a working space that can be filled or filled with a working fluid, which in particular is toroidal.
  • the secondary wheel it is also possible to mechanically drive the secondary wheel to hydrodynamically transfer drive power to the primary wheel by means of the working medium circuit. If the primary wheel is in a mechanical drive connection with the exhaust gas turbine and the compressor, and the secondary wheel in a mechanical drive connection with the output shaft of the internal combustion engine, a hydrodynamic power transmission from the secondary to the primary wheel is always when drive power is transmitted from the output shaft to the compressor, whereas a hydrodynamic power transmission from the primary to the secondary wheel always takes place when drive power from the exhaust turbine to the output shaft and / or the compressor takes place. Also in this embodiment, the hydrodynamic coupling is connected between the exhaust gas turbine and the compressor.
  • the drive connection between the exhaust gas turbine and the compressor is preferably a slip-free connection, in particular an exclusively mechanical connection.
  • the primary wheel of the hydrodynamic coupling is then also in mechanical connection with the exhaust gas turbine and the compressor and is arranged in terms of the power flow between the exhaust gas turbine and the compressor in the drive connection.
  • the exhaust gas turbine more precisely its turbine wheel, the primary wheel and the compressor, more precisely its compressor wheel, can rotate at the same speed and be arranged, for example, together on a shaft.
  • all three components are rotatably supported by a common shaft.
  • a speed-reducing reduction is usually provided between the secondary and the output shaft, which can be formed for example via a gear transmission, in particular spur gear.
  • the primary wheel of the hydrodynamic coupling via a first transmission in a mechanical drive connection with the exhaust gas turbine and a second transmission in a mechanical drive connection with the compressor.
  • the transmissions can be designed, for example, as toothed gearing, in particular in the form of a single gear stage in each case, comprising two toothed wheels, or, for example, also as belt gearing.
  • other forms of transmission not mechanical transmission possible.
  • the gear meshes then advantageously with a first, the exhaust gas turbine associated gear and a second compressor associated with the gear.
  • the gear wheel associated with the exhaust gas turbine can be arranged on a common shaft with the exhaust gas turbine, or be embodied integrally with the exhaust gas turbine.
  • the second, the compressor associated gear may be disposed on a common shaft with the compressor or, for example, be integral with the compressor.
  • the primary wheel of the hydrodynamic coupling can be connected to a pulley or carry one, in particular again on its outer circumference. The pulley is then correspondingly via one or two belts in a drive connection with a pulley associated with the exhaust turbine and a pulley associated with the compressor. The same applies to the gears.
  • the exhaust gas turbine can be, for example, a radial-axial turbine, that is, the exhaust gas flow flows radially from the outside into the exhaust gas turbine and flows in the axial direction of the exhaust gas turbine from the turbine.
  • a spiral is formed in the turbine housing which imparts a large circumferential component to the exhaust gas flow, so that the exhaust gas strikes the turbine wheel essentially in the circumferential direction, causes it to rotate and is deflected in the axial direction of the rotational axis of the turbine wheel and flows away from the turbine wheel ,
  • an additional unit is provided or a plurality of additional units are provided, which / which is driven by means of the exhaust gas turbine of the turbocharger / are.
  • An additional unit may for example be an air compressor of a motor vehicle compressed air system, which feeds compressed air into the vehicle compressed air system.
  • Another unit may be a cooling water pump, which is arranged in the vehicle cooling circuit to circulate the cooling water (or generally a predetermined cooling medium) in the vehicle cooling circuit. With this vehicle cooling circuit, for example, the internal combustion engine and / or the hydrodynamic coupling and / or the exhaust gas can be cooled.
  • a power-controllable is advantageously in the drive connection between the exhaust turbine and the crankshaft or between the crankshaft and the compressor or power-controllable transmission element provided, for example, a controllable or controllable hydrodynamic coupling.
  • the regulation or control of the power transmission in the hydrodynamic coupling can be done for example by deliberately varying the degree of filling of the working space of the hydrodynamic coupling.
  • At least one throttle element for example a throttle ring or a throttle disk, may be provided, which can be introduced into the working space of the hydrodynamic clutch such that the circulation flow of the working fluid in the working space is more or less disturbed by this throttle element.
  • a control unit which corresponds to the hydrodynamic coupling and optionally with other units, for example, the exhaust gas turbine or other control devices is connected.
  • the power transmission from the output shaft of the internal combustion engine to the compressor of the turbocharger can be adjusted to avoid the turbo lag.
  • such a power transmission is always set selectively by means of the control unit, for example by changing the degree of filling of the working space or displacement of the throttle element in the hydrodynamic coupling, if a relatively small exhaust gas flow is present, with which the exhaust gas turbine is acted upon, for example, at low speeds of the internal combustion engine ,
  • the reversal of the direction of power transmission in the hydrodynamic clutch is made automatically without changing its power transmission capability.
  • the exhaust gas turbine which is in a drive connection with the turbocharger and the auxiliary unit or the output shaft of the internal combustion engine, which is also understood to be an output shaft of a transmission connected to the internal combustion engine
  • a conventional turbocharger system comprising a "own” Exhaust gas turbine and a "own” compressor.
  • Such a system would then be a multi-stage supercharged internal combustion engine.
  • a filling-controlled hydrodynamic coupling in the drive connection between the exhaust gas turbine and the output shaft of the internal combustion engine it is also possible to provide a constantly filled hydrodynamic coupling which can be regulated via a throttle element or which is not controllable or controllable.
  • the hydrodynamic coupling in particular radially outside on its secondary wheel, have a toothing which meshes with a gear supported by the engine output shaft or in a drive connection with the engine output shaft in order to form the above-described transmission between the secondary wheel and the output shaft.
  • a gear can also be arranged on a shaft connected to the secondary wheel, in particular the secondary wheel bearing shaft, in particular in the axial direction outside of the working space of the hydrodynamic coupling.
  • the secondary can be relatively stored for example on this shaft - in particular between the impeller of the compressor and the Primary -, that is, although supported by the shaft, but not rotatably connected to the shaft, by providing at least one corresponding sliding bearing and / or rolling bearing between the shaft and the secondary.
  • Alternative storage concepts are conceivable.
  • Figure 1 A first embodiment of an inventive
  • Figure 2 shows a second embodiment of an inventive
  • FIG 1 is very schematically a drive train with an internal combustion engine 1, comprising an output shaft 1.1, shown.
  • the output shaft 1.1 for example in the form of a crankshaft, is connected via a transmission, not shown here, in a drive connection with drive wheels (not shown) of the motor vehicle which is driven by the internal combustion engine 1 or by means of the drive train.
  • the internal combustion engine 1 generates exhaust gas in the combustion of fuel, which is mixed with air from an air duct 4 and ignited, see the schematically illustrated exhaust gas stream 3.
  • the air in the air duct 4 is pre-compressed by the compressor 2.2 of the turbocharger 2.
  • the compressor 2.2 is driven by means of the exhaust gas turbine 2.1 in the exhaust stream 3 with exhaust gas energy.
  • the exhaust gas turbine 2.1 (or its turbine wheel) is rotatably mounted on a shaft which also rotatably supports the compressor 2.2 (or the compressor wheel thereof). Furthermore, this shaft carries the primary wheel 5.1 a hydrodynamic coupling 5, in particular also rotatably.
  • the hydrodynamic coupling 5 has a primary wheel 5.1 axially opposite secondary wheel 5.2, which is relatively mounted on said shaft and forms a toroidal working space 5.3 with the primary wheel 5.1.
  • the hydrodynamic coupling 5 is arranged between the exhaust gas turbine 2.1 and the compressor 2.2.
  • drive power is transferred hydrodynamically from the primary wheel 5.1 to the secondary wheel 5.2 or, in certain operating states, the other way round as well.
  • drive power can be transmitted from the exhaust turbine 2.1 via the hydrodynamic coupling 5 to the output shaft 1.1, or from the output shaft 1.1 via the hydrodynamic coupling 5 to the compressor 2.2 and / or the exhaust gas turbine 2.1, if desired.
  • a control unit 6 For controlling the power transmission, a control unit 6 is provided, which is connected in a controlling or regulating manner with the hydrodynamic coupling 5 and possibly other components.
  • this control unit 6 controls the inflow and / or outflow of working medium into the working space 5.3 and / or the position of a throttling element (not shown) which can be introduced into the working space 5.3 or the circulation flow of working medium in the working space 5.3.
  • the output shaft 1.1 in the embodiment shown in Figure 1 is an accessory.
  • another accessory such as an electric generator, an air compressor or a compressed air compressor of a motor vehicle compressed air system the exhaust gas turbine 2.1, in particular drive the illustrated drive connection with the hydrodynamic coupling 5.
  • Only purely schematically such an accessory is shown in dashed lines and designated by the reference numeral 7.
  • FIG. 2 shows an alternative embodiment of the invention, in which the exhaust gas turbine 2.1 and the compressor 2.2 are arranged separately from one another here, each on its own shaft.
  • the drive connection between the exhaust gas turbine 2.1 and the compressor 2.2 is made via the primary wheel 5.1 of the hydrodynamic coupling 5, which is also a purely mechanical drive connection.
  • the primary wheel 5.1 of the hydrodynamic coupling 5 is arranged on a shaft provided in addition to the shafts of the exhaust gas turbine 2.1 and of the compressor 2.2.
  • the secondary wheel 5.2 of the hydrodynamic coupling 5 is arranged on a further shaft, which in a mechanical drive connection with the Output shaft 1.1 of the internal combustion engine 1 is, in this case via a reduction with two gears.
  • the primary wheel 5.1 and / or the coupling shell 5.4 connected to the primary wheel 5.1, which together with the primary wheel 5.1 surrounds the secondary wheel 5.2, carries a toothing 5.5 on its outer circumference. This toothing 5.5 meshes with the gear wheel associated with the exhaust gas turbine 2.1 and the gear wheel associated with the compressor 2.2.
  • the gear of the exhaust gas turbine 2.1 associated with the same outer diameter or the same pitch diameter as the compressor 2.2 associated gear. It can thereby be achieved that the ratio between the primary wheel 5.1 of the hydrodynamic coupling 5 and the exhaust gas turbine 2.1 is the same as the ratio between the primary wheel 5.1 and the compressor 2.2, so that the compressor 2.2 and the exhaust gas turbine 2.1 rotate at the same speed.
  • the toothing 5.5 has a larger diameter than the meshing with it gears of the exhaust turbine 2.1 and the compressor 2.2, so that the primary wheel 5.1 of the hydrodynamic coupling 5 rotates slower than the exhaust gas turbine 2.1 and the compressor 2.2.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne une chaîne cinématique, en particulier pour véhicules à moteur, comprenant un moteur à combustion interne (1) présentant un arbre de sortie (1.1); un turbocompresseur (2) présentant une turbine à gaz d'échappement (2.1) montée dans le courant de gaz d'échappement (3) du moteur à combustion interne (1), et un compresseur (2.2) entraîné par la turbine à gaz d'échappement (2.1), lequel est disposé dans un conduit d'air (4) aboutissant au moteur à combustion interne (1), en vue de comprimer l'air pour ce moteur. La turbine à gaz d'échappement (2.1) est en liaison d'entraînement avec un groupe auxiliaire (7) ou avec l'arbre de sortie (1.1) du moteur à combustion interne (1), ou peut être commutée dans une telle liaison, afin de transférer la puissance motrice, selon les nécessités, ou instantanément, de la turbine à gaz d'échappement (2.1) au compresseur (2.2) ou à l'arbre de sortie (1.1) et au groupe auxiliaire (7), cependant qu'il est prévu dans la liaison d'entraînement agencée en supplément, un accouplement hydrodynamique (5) comprenant une roue primaire à ailettes (5.1) et une roue secondaire à ailettes (5.2) qui forment un compartiment de travail (5.3) qui est rempli, ou peut être rempli, d'un milieu de travail afin de transférer hydrodynamiquement la puissance motrice de la roue primaire (5.1) à la roue secondaire (5.2); la roue primaire (5.1) étant en liaison d'entraînement avec la turbine à gaz d'échappement (2.1), et la roue secondaire étant en liaison d'entraînement avec le groupe auxiliaire (7) ou l'arbre de sortie (1.1). L'invention est caractérisée en ce que l'accouplement hydrodynamique est monté entre la turbine à gaz d'échappement et le compresseur.
PCT/EP2008/003690 2007-05-08 2008-05-08 Chaîne cinématique, en particulier pour véhicules à moteur WO2008135288A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US12/449,999 US8191371B2 (en) 2007-05-08 2008-05-08 Drive train, particularly for motor vehicles
EP08758414A EP2142776B1 (fr) 2007-05-08 2008-05-08 Chaîne cinématique, en particulier pour véhicules à moteur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022042A DE102007022042A1 (de) 2007-05-08 2007-05-08 Antriebsstrang, insbesondere für Kraftfahrzeuge
DE102007022042.3 2007-05-08

Publications (1)

Publication Number Publication Date
WO2008135288A1 true WO2008135288A1 (fr) 2008-11-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/003690 WO2008135288A1 (fr) 2007-05-08 2008-05-08 Chaîne cinématique, en particulier pour véhicules à moteur

Country Status (4)

Country Link
US (1) US8191371B2 (fr)
EP (1) EP2142776B1 (fr)
DE (1) DE102007022042A1 (fr)
WO (1) WO2008135288A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009038771A1 (de) 2009-08-27 2011-03-03 Voith Patent Gmbh Getriebe für ein Turbo-Compound-System
WO2013156619A1 (fr) 2012-04-20 2013-10-24 Voith Patent Gmbh Support de turbocompound pour relier un système de turbocompound à un moteur à combustion interne

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DE102008005201A1 (de) * 2008-01-18 2009-07-23 Voith Patent Gmbh Turbolader-Turbocompoundsystem
DE102008026023A1 (de) * 2008-05-30 2009-12-03 Voith Patent Gmbh Antriebsstrang und Verfahren zum Versorgen eines Druckluftsystems
US9932890B2 (en) * 2008-10-30 2018-04-03 Volvo Lastvagnar Ab Device and method for automatically adjusting torque transmitting ability of a turbocompound transmission
DE102009040623A1 (de) * 2009-09-08 2011-03-10 Hengst Gmbh & Co. Kg Fliehkraftabscheider einer Brennkraftmaschine
DE102010046048A1 (de) * 2010-09-22 2012-03-22 Voith Patent Gmbh Antriebsvorrichtung
DE102011110205A1 (de) 2011-08-16 2013-02-21 Voith Patent Gmbh Antriebsstrang, insbesondere eines Kraftfahrzeugs
CN103061859B (zh) * 2012-12-31 2016-07-06 长城汽车股份有限公司 发动机涡轮增压器与水泵集成装置
EP2886387A3 (fr) * 2013-12-23 2015-12-23 Rolls-Royce Corporation Moteur/générateur à double redondance pour un moteur
DE102014107126A1 (de) * 2014-05-20 2015-11-26 Harald Wenzel Mehrstufige Verdichteranlage zur Erzeugung eines komprimierten Gase
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DE102007022042A1 (de) 2008-11-13
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US8191371B2 (en) 2012-06-05
US20110030370A1 (en) 2011-02-10

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